Method of making recesses in metallic workpieces for use torque transmitting apparatus

ABSTRACT

A selected portion of a surface of a metallic workpiece such as the end surface of a tubular workpiece, is provided with one or more recesses by resorting to a tool having a preferably pointed tip and being driven into the surface to displace the material of the workpiece substantially transversely of the thus obtained recess. The latter can be used to facilitate the establishment of a separable connection between the workpiece and a substantially disc-shaped section of a cover or housing in a friction clutch for use in motor vehicles. The tool can be left in the recess to serve as a locating or centering device for the workpiece.

BACKGROUND OF THE INVENTION

The invention relates to improvements in methods of making recesses inat least partially metallic workpieces. More particularly, the inventionrelates to improvements in methods of making recesses (e.g., in the formof tapped or untapped blind holes or through holes) in workpieces whichcan be used in torque transmitting apparatus, for example, in thehousings or covers of friction clutches for use in motor vehicles.

As a rule, a recess in a metallic workpiece is obtained by removingmaterial from the workpiece, e.g., by resorting to a drill or to anothersuitable material removing tool. If the workpiece is to be provided withan internal thread, the treatment with a drill or with another materialremoving tool (which has been used to form a recess) must be followed bya treatment with a second tool which cuts a thread into the surfacesurrounding the recess. An internal thread is necessary if the recess isto receive a portion of an externally threaded shank forming part of ascrew, bolt, spindle, feed screw, pin, post or the like. For example, itis often necessary to accurately center the workpiece relative toanother part by resorting to so-called alignment, locating or centeringpins (also called fixing or stead pins), dowel pins, drift pins orplugs, set pins or the like. A centering pin must be installed in arecess with a very high degree of accuracy in order to ensure that thethus coupled and centered parts are secured to each other with a minimumof play, i.e., within an acceptable range of tolerances. Such accuracycan be achieved by resorting to material removing and surface smoothingtools in the form of reamers or the like. All this contributessignificantly to the cost of the workpieces, of the combinations of suchworkpieces with one or more additional workpieces as well as of themachines, apparatus or other devices in which the recessed workpiecesare put to use. In addition, it is often difficult to dismantle anapparatus, machine or another device which employs one or moreworkpieces having one or more recesses which are obtained as a result ofremoval of metallic material from a blank or from a semifinishedcomponent of a friction clutch or the like.

OBJECTS OF THE INVENTION

An object of the invention is to provide a method of making recesses(such as tapped or untapped blind holes or through holes) in metallicworkpieces in a simple and inexpensive manner.

Another object of the invention is to provide a method which renders itpossible to avoid removal of material from a workpiece in the course ofa recess forming or making operation.

A further object of the invention is to provide a method which can beutilized for the making of recesses in workpieces including orconstituting blanks or preforms of sheet metal.

An additional object of the invention is to provide a method whichrenders it possible to make recesses with a high degree of accuracy sothat the recesses can accept centering pins, other types of pins,screws, bolts or other male parts with a minimum of play or with no playat all.

Still another object of the invention is to provide a method of makingrecesses in the end faces of relatively thin workpieces in the form ofcylinders, tubes, pipes, sheets or panels in such a way that thediameter or another maximum transverse dimension of a recess at leastmatches but can exceed the wall thickness of the workpiece.

A further object of the invention is to provide a novel and improvedmethod of treating blanks which can be utilized for the making of coversor housings of friction clutches for use in motor vehicles.

Another object of the invention is to provide a method which can beresorted to for accurately assembling component parts of covers orhousings for use in torque transmitting apparatus, such as frictionclutches in motor vehicles.

A further object of the invention is to provide a method of makingrecesses which can be practiced by resorting to simple and readilyavailable tools, implements and apparatus.

An additional object of the invention is to provide a torquetransmitting apparatus at least one component of which has been treatedin accordance with the above outlined method and which can be readilyassembled or partially or fully dismantled in a time saving manner.

Another object of the invention is to provide a relatively complexaggregate which can be readily assembled or dismantled because one ormore of its components were treated in accordance with the aboveoutlined method.

Still another object of the invention is to provide a torquetransmitting apparatus which employs a composite flywheel assembly and afriction clutch utilizing at least one component which has been treatedin accordance with the above outlined method.

A further object of the invention is to provide a torque transmittingapparatus at least certain parts of which can be produced, finished,assembled and/or otherwise processed with substantial savings in energyand which is constructed and assembled in such a way that at least amajority of its constituents can be readily separated from each otherfor inspection, repair or replacement so that each set of partsconsisting of the same material can be recycled in an ecologicallyacceptable manner.

Another object of the invention is to provide a torque transmittingapparatus which can be assembled, inspected, repaired and/or dismantledwith greater facility and at a lower cost than heretofore known torquetransmitting apparatus.

An additional object of the invention is to provide a torquetransmitting apparatus which can be assembled with considerable savingsin primary energy and with minimal waste in metallic material.

Still another object of the invention is to provide a method whichrenders it possible to provide one or more workpieces with tapped oruntapped recesses without any contamination of the surrounding area.

A further object of the invention is to provide a method which rendersit possible to provide metallic workpieces with recesses free ofshavings and/or any other foreign particles necessitating collectionand/or expulsion prior to putting the thus treated workpieces to actualuse.

Another object of the invention is to provide a method which renders itpossible to provide a metallic or partially metallic workpiece with oneor more recesses without the need for cooling the workpiece or withminimal cooling.

An additional object of the invention is to provide a method whichrenders it possible to provide a metallic or at least partially metallicworkpiece with one or more recesses without the need for lubrication oftools serving to provide the workpiece with a blind hole, a tapped holeor another recess.

Still another object of the invention is to provide a method whichrenders it possible to reduce the overall weight of a finished workpieceand which can be practiced in such a way that the tools and/orimplements which are used to make one or more recesses can be put to usein, or in conjunction with, the thus treated workpiece.

A further object of the invention is to provide a composite flywheelassembly, particularly for use in torque transmitting apparatus of thetype employed in motor vehicles, which is more compact, particularly inthe radial direction, than heretofore known flywheel assemblies.

Another object of the invention is to provide a torque transmittingapparatus which is constructed and assembled in such a way that thespace heretofore occupied by conventional flywheel assemblies can be putto use to accommodate other components of such apparatus.

An additional object of the invention is to provide a novel and improvedcover or housing for connection to the diaphragm spring, damper ordampers, clutch disc, pressure plate and/or other components of afriction clutch for motor vehicles.

SUMMARY OF THE INVENTION

One feature of the present invention resides in the provision of amethod of making a recess (e.g., a blind hole or a through hole) in asurface of a workpiece containing a metallic material. The improvedmethod comprises the step of driving into the surface of the workpiece amaterial displacing tool which includes a trailing portion having alarger first cross-sectional area and a front portion or leader having asmaller second cross-sectional area. The driving step includes advancingthe tool in the longitudinal direction thereof, namely in a directionfrom the trailing portion toward the leader so that the leaderpenetrates a selected portion of the surface of the workpiece anddisplaces the material of the workpiece at least substantiallytransversely of the aforementioned direction.

In many instances, the recess will have to be formed in an end surfaceof a workpiece which has a predetermined length (as measured from theend surface). The advancing step of such method can include moving thetool substantially lengthwise of the workpiece.

If the workpiece has a predetermined minimum wall thickness prior to thetool advancing step and the surface is an end surface of the workpiece,the driving step can include utilizing a tool which is dimensioned toprovide the surface of the workpiece with a recess having a maximumtransverse dimension at least matching the minimum wall thickness, i.e.,the maximum transverse dimension (such as the diameter of a circularrecess) can exceed the minimum wall thickness of the workpiece.

The method can further comprise the step of fixedly holding theworkpiece adjacent the selected portion of the surface, at least in thecourse of the advancing step.

If the recess is to be made in an end portion of a tubular workpiece,the aforementioned surface can constitute an end surface of the endportion of such tubular workpiece.

The method can further comprise the step of converting a blank (such asa piece of sheet metal) into the workpiece prior to the driving step,and the converting step can include drawing, forging and/or otherwiseshaping the blank. The blank can be converted into a tubular (e.g., anat least substantially cylindrical) workpiece.

The workpiece can have at least one additional surface, and the methodcan further comprise the step of calibrating, at least in part, the atleast one additional surface. For example, the recess might be necessaryin an end face of a tubular workpiece further having an internal surfaceand an external surface; the calibrating step can include calibratingthe internal and/or the external surface of such workpice.

If the workpiece is designed to have an axis of rotation, the directionof advancement of the leader of the tool into a surface of suchworkpiece can be at least substantially parallel to the axis ofrotation.

The method can further comprise the step of leaving at least the leaderof the tool in the recess. Alternatively, the method can comprise theadditional step of withdrawing the tool from the recess.

The driving step can include employing a tool which imparts to therecess a substantially circular, polygonal, oval or othercross-sectional outline.

The method can comprise the additional step of anchoring an element inthe recess. The anchored element can include or constitute a locating orcentering pin. Such anchored element can constitute a portion of or theentire material displacing tool, i.e., the tool can be left in thefreshly formed recess to constitute an anchoring, locating, centering orlike element.

The method can also comprise the additional step of providing theworkpiece with an internal thread in the recess. Such additional stepcan include employing a tapping tool which does not remove shavings fromthe workpiece, e.g., a so-called thread rolling tool or an analogoustool. The tapping tool can be constituted by the aforediscussed materialdisplacing tool which is used to make the recess.

The method can also include the step of anchoring the workpiece of amale fastener including a first portion in the recess and an externallythreaded second portion outside of the recess. Such method can alsocomprise the step of moving at least one nut into mesh with theexternally threaded second portion of the fastener. The anchoring stepcan include employing a male fastener having an externally threadedfirst portion in mesh with the workpiece. The male fastener can includeor constitute a screw or a bolt. For example, the anchoring step caninclude employing a male fastener having a first portion which displacesthe material of the workpiece during introduction into the workpiece.The method can also comprise the step of withdrawing the materialdisplacing tool from the recess prior to the anchoring step.

At least a portion of the workpiece can consist of sheet metal, and thedriving step can include making in the sheet metal a recess in the formof a through hole or a blind hole.

Another feature of the invention resides in the provision of a metalliccomponent which can constitute an element of a friction clutch and has asurface provided with at least one recess which is formed in accordancewith the aforediscussed method, i.e., as a result of driving into thesurface of the metallic component a material displacing tool (of thetype including a trailing portion having a larger first cross-sectionalarea and a front portion or leader having a smaller secondcross-sectional area) in such a way that the leader has penetrated thesurface in a direction from the trailing portion toward the leader(which latter can constitute or include a substantially conical orpyramidal tip) and the tool has displaced the material of the metalliccomponent at least substantially transversely of the aforementioneddirection from the trailing end toward the leader. The metalliccomponent can include or constitute or form part of a housing or casing.For example, the housing or casing can include a tubular (e.g., at leastsubstantially cylindrical) section having an end portion, and a secondsection which is separably affixed to the tubular section. Theaforementioned recess surface is or can be provided on the tubularsection of the housing or casing.

A further feature of the invention resides in the provision of afriction clutch which comprises a composite flywheel assemblyconnectable to a combustion engine and including a secondary flywheel,and a tubular (e.g., an at least substantially cylindrical) metalliccomponent which is carried by the secondary flywheel and has a surfaceprovided with a plurality of tapped recesses (e.g., in the form of blindholes) which are spaced apart from each other circumferentially of thetubular component. At least one of the recesses is obtained inaccordance with the aforediscussed method, i.e., as a result of drivinginto the surface a material displacing tool, including a trailingportion having a larger first cross-sectional area and a leader or frontportion having a smaller second cross-sectional area, in such a way thatthe leader has penetrated into the surface in a direction from thetrailing portion toward the leader and the tool has displaced thematerial of the metallic component at least substantially transverselyof the aforementioned direction. The clutch further comprises a housingor cover section adjacent the surface of the metallic component, andthreaded fasteners (e.g., in the form of bolts or screws) which securethe housing or cover section to the metallic component and have portions(e.g., in the form of externally threaded shanks) extending into therecesses. The housing or cover section can extend substantially radiallyof and can be separably secured to the tubular metallic component. Suchfriction clutch can further comprise a diaphragm spring or an analogousresilient biasing device which is tiltably carried by the housing orcover section. The secondary flywheel is rotatable about a predeterminedaxis and the friction clutch can further comprise a pressure plate andmeans for non-rotatably but axially movably securing the pressure plateto the tubular metallic component for movement in the direction of theaxis of the secondary flywheel. Such friction clutch can furthercomprise energy storing elements which are deformable in thecircumferential direction of the composite flywheel. The tubularcomponent of such friction clutch can be provided with means (e.g., inthe form of arms) for deforming or stressing the energy storingelements. The energy storing elements can include or constituteelongated arcuate coil springs.

An additional feature of the present invention resides in the provisionof a torque transmitting apparatus which comprises a composite housingor cover rotatable about a predetermined axis and including a componentextending in the direction of the axis and having a surface providedwith at least one recess formed in accordance with the aforediscussedmethod, i.e., such recess can be obtained as a result of driving intothe surface a material displacing tool (including a trailing portionhaving a larger first cross-sectional area and a front portion or leaderhaving a smaller second cross-sectional area) in such a way that theleader has penetrated the surface in a second direction from thetrailing portion toward the leader and the tool has displaced thematerial of the component at least substantially transversely of thesecond direction. The second direction is or can be at leastsubstantially parallel to the direction of extension of theaforementioned component. The housing can constitute a cover of afriction clutch for use in motor vehicles.

An additional feature of the present invention resides in the provisionof an apparatus for compensating for torsional stresses. Such apparatuscomprises a first flywheel which is connectable with an engine (e.g.,with the crankshaft or an analogous output element of the engine in amotor vehicle), and a second flywheel connectable with an input elementof a transmission (such as a variable-speed transmission in the powertrain between the engine and the wheels of a motor vehicle). Theflywheels are rotatable relative to each other and the apparatus furthercomprises at least one damper having means (such as the aforediscussedarcuate coil springs) for yieldably opposing rotation of the flywheelsrelative to each other. Such apparatus preferably further comprises atleast one antifriction bearing which is interposed between theflywheels, and a metallic component which is affixed to one of theflywheels (particularly to the second flywheel) and extends in thedirection of the axis of rotation of the one flywheel. The component hasa surface provided with at least one recess formed in accordance withthe aforediscussed method, namely as a result of driving into thesurface a material displacing tool (including a trailing portion havinga larger first cross-sectional area and a front portion or leader havinga smaller second cross-sectional area) in such a way that the leader haspenetrated the surface in a second direction from the trailing portiontoward the leader and the tool has thereby displaced the material of thecomponent at least substantially transversely of the second direction.The apparatus further comprises a housing portion or cover portion whichis connectable to the aforediscussed component, e.g., by fasteners oneof which extends into the aforediscussed recess. The apparatus of thejust outlined character can further comprise means (e.g., bolts oranalogous threaded fasteners) for affixing one of the flywheels(normally the first flywheel) to an output element of a combustionengine.

Still another feature of the invention resides in the provision of afriction clutch which comprises a housing or cover made at least in partof sheet metal and including an at least substantially cylindrical firstsection having an axial end and a second section disposed at the axialend and extending at least substantially radially of the first section,threaded fasteners which separably connect the two sections to eachother, a pressure plate which is non-rotatably affixed to the housing orcover for movement in the axial direction of the first section, andmeans (e.g., including a diaphragm spring) for biasing the pressureplate axially of the first section. The axial end of the first sectionpreferably includes a surface which is provided with recesses extendingsubstantially axially of the first section and formed in accordance withthe aforediscussed method, namely as a result of driving into thesurface a material displacing tool which has displaced the material ofthe first section substantially radially of the respective recess.

An additional feature of the invention resides in the provision of afriction clutch comprising a component (such as a cover or housing)including a substantially cylindrical section, a composite flywheelassembly including a flywheel connectable with an output element of acombustion engine, energy storing elements acting in the circumferentialdirection of and reacting against the flywheel assembly, and torquetransmitting elements provided on the substantially cylindrical sectionand bearing against the energy storing elements. The aforementionedcomponent can comprise a second section which is separably affixed tothe substantially cylindrical section. The latter consists of or canconsist, at least in part, of a metallic sheet material. Thesubstantially cylindrical section preferably includes a surface which isadjacent the second section and is provided with recesses at least oneof which is obtained as a result of displacing the material of thesubstantially cylindrical section substantially radially of the axis ofthe at least one recess, preferably entirely without removal of shavingsand/or otherwise configurated pieces of the substantially cylindricalsection.

The novel features which are considered as characteristic of theinvention are set forth in particular in the appended claims. Theimproved method itself, however, together with additional features andadvantages thereof, will be best understood upon perusal of thefollowing detailed description of certain presently preferred specificembodiments with reference to the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a fragmentary axial sectional view of a torque transmittingapparatus including a friction clutch having a component with a surfacewhich is recessed in accordance with the method of the presentinvention;

FIG. 2 is an enlarged fragmentary front elevational view of thecomponent substantially as seen in the direction of arrow II in FIG. 1,and further showing portions of means for clamping or holding thecomponent during the making of recesses in its surface;

FIG. 3 is a transverse sectional view substantially as seen in thedirection of arrows from the line III--III in FIG. 2, and further showsa portion of a material displacing tool which is used to make recessesin the surface of the component shown in FIG. 2;

FIG. 4 is an enlarged view of a detail within the phantom-line circle IVof FIG. 3 and further illustrates a portion of a modified materialdisplacing tool; and

FIG. 5 is a fragmentary axial sectional view of still another materialdisplacing tool.

DESCRIPTION OF PREFERRED EMBODIMENTS

Referring first to FIG. 1, there is shown a torque transmittingapparatus which includes a composite flywheel assembly 1 with a primaryor first flywheel 2 and a coaxial secondary or second flywheel 3, and afriction clutch 4 having a clutch plate or clutch disc 5 with frictionlinings 5a adjacent an annular friction surface 3a of the secondaryflywheel 3. The primary flywheel 2 can be separably affixed (i.e.,detachably connected together) to the output element (e.g., acrankshaft) of an internal combustion engine, and the clutch disc 5 hasa hub 5b which can be non-rotatably affixed to the input element of avariable speed transmission in a motor vehicle. Reference may be had,for example, to commonly owned U.S. Pat. No. 5,156,249 granted Oct. 20,1992 to Friedmann for "Torque transmitting apparatus with axiallydeformable primary flywheel" and/or to commonly owned U.S. Pat. No.5,160,007 granted Nov. 3, 1992 to Reik and Jackel for "Apparatus fortransmitting torque in the power trains of motor vehicles". Thedisclosures of these patents and of all other publications mentioned inthe specification of the present application are incorporated herein byreference.

The friction clutch 4 further comprises a pressure plate 31 which isnon-rotatably but axially movably coupled to the secondary flywheel 3 bya composite clutch housing or cover 30 in a manner to be described ingreater detail hereinafter. When the friction clutch 4 is engaged, thepressure plate 31 is biased toward and against the adjacent frictionlining 5a of the clutch disc 5 so that the other friction lining 5a isurged against the surface 3a of the flywheel 3 and the latter rotatesthe input element of the transmission by way of the hub 5b when thesecondary flywheel 3 receives torque from the primary flywheel 2, i.e.,from the output element of the engine.

The illustrated clutch disc 5 constitutes but one of a large number ofdevices which can be used in the clutch 4 (or in an analogous frictionclutch) to transmit torque to the input element of the transmission whenthe clutch 4 is engaged. For example, the rigid annular flange 5c of theillustrated clutch disc 5 can be replaced with a flange which isprovided with one or more dampers and/or friction generating devicesoperating between the friction linings 5a and the hub 5b. Alternatively,or in addition to such damper or dampers and/or friction generatingdevices, the clutch disc 5 can be equipped with means for yieldablymounting the friction linings 5a on the flange 5c. Still further, theseparately produced rivets 5d which are used to secure the frictionlinings 5a to the flange 5c of the illustrated clutch disc 5 can bereplaced with rivets which are of one piece with the flange 5c. All suchfeatures are described and shown in numerous United States and foreignpatent applications and patents of the assignee of the presentapplication. Reference may be had, by way of example only, to commonlyowned U.S. Pat. No. 5,161,660 granted Nov. 10, 1992 to Huber for "Clutchplate with plural dampers" which describes and shows that the connectionbetween the friction linings and the hub of a clutch disc can compriseone or more dampers and/or friction generating devices.

The torque transmitting apparatus of FIG. 1 further comprises anantifriction ball bearing 6 here shown as comprising a single row ofspherical antifriction rolling elements 6b between an inner race 16 andan outer race 17. The inner race 16 surrounds an adjacent part of theflywheel 2 and the outer race 17 is surrounded by an adjacent part ofthe flywheel 3. The entire bearing 6 is installed radially inwardly ofaxially parallel holes 7 which are provided in the primary flywheel 2 toreceive the externally threaded shanks of fasteners 8 serving toseparably affix the flywheel 2 to the output element of the engine in amotor vehicle. The purpose of the bearing 6 is to ensure that theflywheels 2, 3 are coaxial with each other and that they can turnrelative to one another with a minimum of resistance other than thatoffered by constituents which are specifically provided in the torquetransmitting apparatus of FIG. 1 for such purpose, i.e., to oppose and,if necessary, limit the extent of angular movement of the flywheels 2and 3 relative to one another.

The illustrated antifriction bearing 6 is provided with a relativelysimple cap-shaped sealing element 6a which can contain a supply oflubricant for the rolling elements 6b and/or serves as a thermalinsulator between the sensitive parts of the bearing 6 and the secondaryfriction wheel 3. Such thermal insulation is desirable and oftennecessary because the secondary flywheel 3 is likely to be heated to anelevated temperature when the friction linings 5a of the clutch disc 5are permitted to slip relative to the friction surface 3a at that sideof the flywheel 3 which faces away from the flywheel 2. The sealingelement 6a can further serve to prevent uncontrolled transfer ofsubstantial amounts of heat from the secondary flywheel 3 to the primaryflywheel 2.

The means for opposing rotation of the flywheels 2 and 3 relative toeach other (or for opposing at least certain stages of such rotation)includes a damper 9 having arcuate energy storing elements 10 in theform of coil springs extending circumferentially of the flywheelassembly 1 and being installed in the radially outermost portion orcompartment 12 of a ring-shaped chamber 11 defined by the primaryflywheel 2. At least a portion of the chamber 11 is filled with asuitable lubricant (oil or grease), preferably a lubricant (fat orgrease) of pasty consistency such that it is highly unlikely to assumethe consistency of a low-viscosity liquid, even if heated to an elevatedtemperature.

The primary flywheel 2 in the torque transmitting apparatus of FIG. 1comprises a main portion 13 which is preferably made of a suitablemetallic sheet material but can also constitute a forging or anextrusion. The radially inner part 14 of the main portion 13 of theprimary flywheel 2 is provided with the aforementioned holes 7 for theshanks of the fasteners 8 which separably affix the flywheel 2 (andhence the entire torque transmitting apparatus) to the output element ofan engine. The chamber 11 and its compartment 12 are provided mainly inthe radially outer part 18 of the main portion 13. The radially innerpart 14 of the main portion 13 carries a separately produced tubularcarrier 15 having an end portion 15a which is surrounded by the innerrace 16 of the antifriction bearing 6. The radially outer portion of thecarrier 15 is provided with holes 7a in register with the holes 7 in theradially inner part 14 of the main portion 13. The end portion 15a ofthe tubular carrier 15 has an external shoulder serving as an abutmentfor one axial end of the inner race 16, namely that end which is remotefrom the sealing element 6a.

The illustrated relatively complex secondary flywheel 3 can be replacedwith a simpler (e.g., with a substantially flat washer-like) secondaryflywheel without departing from the spirit of the present invention. Theradially inner portion of the secondary flywheel 3 has an axial passagewhich receives the outer race 17 of the antifriction bearing 6 as wellas the sealing element 6a and is provided with a shoulder for theadjacent axial end of the outer race 17.

The radially outer part 18 of the main portion 13 of the primaryflywheel 2 surrounds a substantial portion of each coil spring 10 andits outermost portion extends axially of the composite flywheel assembly1 in a direction away from the engine (which is assumed to be located tothe left of the flywheel 2, as viewed in FIG. 1) so that it is disposedradially outwardly of the compartment 12. The internal surface of suchaxially extending portion of the radially outer part 18 of the mainportion 13 can be actually contacted by the adjacent portions of thecoil springs 10, especially when the flywheel 2 is caused to rotate atan elevated speed so that the springs 10 are acted upon by a pronouncedcentrifugal force. Alternatively, the inner side of the axiallyextending portion of the radially outer part 18 of the main portion 13can be provided with a wear-resistant liner in the form of a trough orthe like so that the radially outer portions of the coil springs 10cannot move into actual contact with the flywheel 2. Reference may behad, for example, to the aforementioned commonly owned U.S. Pat. No.5,156,249 to Friedmann.

The primary flywheel 2 further comprises an in part radially extendingwall 19 which is welded (as at 20) to the adjacent axially extendingportion of the radially outer part 18 of the main portion 13 and definesa relatively small portion of the compartment 12 for the coil springs 10forming part of the damper 9. The wall 19 can be made of sheet metal.The radially outer part 18 and the wall 19 are provided with confrontingarcuate sockets for portions of the coil springs 10. Furthermore, theradially outer part 18 and the wall 19 are provided with aligned axiallyextending partitions which are disposed between pairs of neighboringcoil springs 10 and serve to stress the coil springs when the flywheel 2is caused to turn relative to the flywheel 3 and/or vice versa.Reference may be had, for example, to the aforementioned commonly ownedU.S. Pat. No., 5,156,249 to Friedmann which shows that the externalsurfaces of the radially outer part of the main portion of the wall ofthe primary flywheel can be provided with depressions in the form ofcircumferentially spaced-apart pockets which define the aforementionedinternal partitions and cooperate with suitably configurated arms of theclutch housing or cover to ensure that the coil springs store at leastsome energy in response to rotation of at least one of the two flywheelsrelative to the other flywheel. The illustrated wall 19 is located atthat side of the main portion 13 of the primary flywheel which facesaway from the engine.

As shown in FIG. 1, the radially outer part 18 of the main portion 13can surround a larger part of the damper 9 (especially the coil springs10) than the wall 19. The substantially tubular or sleeve-like radiallyinner portion 19a of the wall 19 extends axially of the assembly 1 andaway from the main portion 13.

Each of the coil springs 10 is received in a discrete arcuate portion ofthe compartment 12 between two axially extending partitions of theradially outer part 18 and two axially extending partitions of the wall19. The aforementioned external pockets of the radially outer part 18and wall 19 can be omitted if the partitions between the end portions ofneighboring coil springs 10 are separately machined parts which areaffixed to the internal surfaces of the part 18 and wall 19.

The friction clutch 4 further comprises a support 22 for torquetransmitting elements in the form of arms 21 extending into thecompartment 12 between pairs of neighboring coil springs 10. The support22 is connected with and serves to transmit torque to the flywheel 3 inresponse to rotation of the flywheel 2 by the engine of the motorvehicle. The arms 21 extend substantially radially outwardly from thesubstantially disc-shaped central portion of the support 22. In lieu ofemploying a separately produced support 22, the damper 9 can beconstructed in such a way that radially inner portions 23 of the arms 21are of one piece with the secondary flywheel 3 and cause the flywheel 3to rotate in response to rotation of the primary flywheel 2. The coilsprings 10 of the damper 9 then react against the aforediscussedpartitions of the radially outer part 18 of the main portion 13 of theprimary flywheel 2 and bear against the adjacent arms 21. Reference maybe had, for example, to commonly owned copending German patentapplication Serial No. P 42 12 954.0 and to the corresponding U.S.patent application Ser. No. 08/044,031 which describe and show asecondary flywheel of one piece with torque transmitting elementscorresponding to the arms 21 shown in FIG. 1 of the present application.When the torque transmitting apparatus is not in use (i.e., when theflywheels 2 and 3 are not caused to rotate in order to transmit torquebetween the engine and the secondary flywheel 3), each arm 21 is locatedbetween a pair of aforementioned partitions, namely a partition on theradially outer part 18 of main portion 13 of the primary flywheel 2 anda partition on the wall 19 of the primary flywheel.

In accordance with a further modification which is not specificallyshown in the drawing, the support 22 for the arms 21 need not bedirectly coupled to the secondary flywheel 3 but rather to one or moreparts which, in turn, can transmit torque to the secondary flywheel.Still further, each of the arms 21 can be a separately produced partwhich is indirectly coupled with and can transmit torque to thesecondary flywheel 3.

The area of that side or surface of the secondary flywheel 3 which islocated opposite to and faces away from the friction surface 3a (i.e.,which faces the main portion 13 of the primary flywheel 2) can beenlarged to thus ensure more satisfactory dissipation of heat which isgenerated when the left-hand friction lining 5a of the clutch disc 5rubs against the surface 3a while at least one of the clutchconstituents 3 and 5 rotates relative to the other. The left-handsurface of the secondary flywheel 3 can be enlarged by providing it withrhomboidal, diamond-shaped and/or otherwise configurated projectionsand/or depressions (not specifically shown) in the course of acalibrating operation upon the secondary flywheel. The latter can bemade of steel and can constitute a stamping. Alternatively, theleft-hand surface of the secondary flywheel 3 can be enlarged byproviding it with one or more spiral-shaped and/or otherwiseconfigurated grooves. Such groove or grooves can be formed by resortingto mechanical treatment with a suitable grooving or channelling tool orby causing an annular milling cutter (not shown) to penetrate into theflywheel 3 in such position that its axis is parallel or substantiallyparallel to (rather than coinciding with) the axis of rotation of thesecondary flywheel. It has been found that any one of the just outlinedsurface enlarging techniques can be resorted to in order to ensuresufficient dissipation of heat by the secondary flywheel 3, i.e., toavoid an overheating of the primary flywheel 2 and/or of theantifriction bearing 6 and/or of one or more other sensitive parts ofthe torque transmitting apparatus. If the secondary flywheel 3 is acasting, the area of its left-hand surface can be enlarged (for thepurpose of more satisfactory dissipation of heat) during making of thesecondary flywheel, i.e., in the mold.

The chamber 11 and its compartment 12 are preferably sealed from thesurrounding atmosphere in order to reduce the likelihood of escape ofthe preferably pasty lubricant of the coil springs 10 of the damper 9.FIG. 1 shows two sealing devices 24 and 25. The sealing device 24 is orresembles a ring-shaped part and is made of one piece; its radiallyinner part engages and is centered by an externally extending shoulderof the radially inner part 14 of main portion 13 of the primary flywheel2. Such radially inner part of the sealing device 24 extendssubstantially radially outwardly into the axially extending annularclearance between the part 14 and the (preferably) enlarged left-handsurface of the secondary flywheel 3, i.e., opposite the friction surface3a. The radially outer part of the sealing device 24 abuts, or is atleast rather closely adjacent, a portion of the aforementioned support22 for the arms 21 which engage the coil springs 10 of the damper 9. Thesupport 22 maintains, or can maintain, the adjacent radially outer partof the sealing device 24 in a predetermined (optimum) axial positionrelative to the flywheels 2 and 3. The sealing device 24 can constituteor can act as a diaphragm spring which reacts against the primaryflywheel 2 and bears against the support 22 in order to seal thecorresponding portion of the chamber 11 from the atmosphere,particularly from openings which are provided in the main portion 13 ofthe primary flywheel 2. In order to be effective as a seal, the device24 is installed between the primary flywheel 2 and the support 22 on thesecondary flywheel 3 in at least partially stressed condition (as seenaxially of the flywheels 2 and 3).

The primary flywheel 2 carries a customary starter gear 26 which iswelded and/or otherwise reliably secured to the sleeve-like portion 19aof the wall 19.

The illustrated second sealing device 25 for the chamber 11 is acomposite device including a first annular portion 27 having asubstantially L-shaped cross-sectional outline and a substantiallydisc-shaped or washer-like second portion 28 which preferablyconstitutes a diaphragm spring and is stressed in the axial direction ofthe flywheels 2 and 3. The radially outer part of the second portion 28reacts against that surface of the wall 19 which confronts the coilsprings 10 in the radially outermost portion or compartment 12 of thechamber 11, and the radially inner part of the second portion 28 bearsagainst the first portion 27 of the second sealing device 25. In thismanner, the first portion 27 is biased in a direction toward the engine,i.e., toward the main portion 13 of the primary flywheel 2. The anglebetween the axially and radially extending components or legs of thefirst portion 27 is preferably at least slightly less than 90°, i.e.,the portion 27 can have a substantially V-shaped cross-sectionaloutline. The axially extending leg of the portion 27 of the secondsealing device 25 which is shown in FIG. 1 is a preferably tight fit onand is supported by the left-hand end of the sleeve-like portion orsection 29 forming part of the clutch cover 30.

The devices 24 and 25 need not hermetically seal the respective portionsof the annular chamber 11 from the atmosphere because the lubricantwhich is confined in and fills at least a portion of the chamber 11 ispreferably of pasty consistency, i.e., its viscosity is high. Grease hasbeen found to constitute a satisfactory lubricant for the coil springs10 in the compartment 12 of the chamber 11. As a rule, the sealingdevices 24, 25 serve primarily as a means for preventing penetration ofdust and/or other foreign matter from the surrounding atmosphere intothe chamber 11. They will serve to prevent the confined lubricant fromescaping the chamber 11 only in the rather unlikely event that theviscosity of the lubricant decreases well below the anticipated value.The confined lubricant cannot escape the compartment 12 by flowingradially outwardly because the axially extending portion of the radiallyouter part 18 of main portion 13 of the primary flywheel 2 is welded orsoldered (at 20) to the adjacent radially outer portion of the wall 19.

The friction clutch 4 and its disc 5 preferably constitute oneconstituent of a preassembled unit which further includes the compositeflywheel 1 and the antifriction bearing 6. Such design of the improvedtorque transmitting apparatus has been found to be highly desirable andadvantageous because the unit can be assembled at the manufacturingplant and can be shipped or otherwise delivered to an automobile makingor assembling plant in a condition ready for attachment of the primaryflywheel 2 to the output element of the engine. The making of thepreassembled unit reduces the cost of assembling, shaping and/or storageas well as the cost of securing the unit to the input element of theengine. For example, by assembling the unit including the flywheels 2,3, the friction clutch 4 and its disc 5, and the antifriction bearing 6,it is possible to dispense with several operations or steps which arenecessary if all parts of the torque transmitting apparatus are to beassembled with each other and installed between the output element ofthe engine and the input element of the variable speed transmission atthe automobile making or assembling plant. For example, the clutch disc5 can be centered between the secondary flywheel 3 and the cover 30 ofthe friction clutch 4 at the plant where the improved apparatus is madeand where the parts 2, 3 and 4, 5 are assembled to form a compact unitwhich is ready for shipment, storage or attachment to the output elementof the engine. Moreover, the clutch disc 5 can be installed between thecover 30 and the secondary flywheel 3 with a higher degree of accuracyand within a shorter period of time than if such assembly of the part 5with the parts 30 and 3 were to be carried out in the automobile makingor assembling plant. In accordance with heretofore known techniques,centering of the clutch disc 5 between a flywheel and a clutch covernecessitates the utilization of a special tool, such as a mandrel, whichcan further serve to center the flywheel(s) on the output element of theengine. The fasteners which are used to secure a flywheel, forming partof a conventional torque transmitting apparatus, to the output elementof an engine are installed on the flywheel at the time when suchfasteners are to be driven into, or otherwise secured to, the outputelement. Still further, one can dispense with the step of removing thecentering mandrel upon completion of attachment of a conventional torquetransmitting apparatus of the input element of an engine. In addition,one dispenses with the heretofore necessary (and often rather complex)procedure of securing the friction clutch to the flywheel or to theflywheel assembly subsequent to attachment of the flywheel or flywheelassembly to the output element of the engine.

The provision of a preassembled unit, which further includes theantifriction bearing 6 or an analogous bearing, also contributes tosimplicity of the improved torque transmitting apparatus and toconvenient installation of such apparatus in a motor vehicle. Thebearing 6 is properly centered on the end portion 15a of the carrier 15forming part of the primary flywheel 2 and within the axial passage inthe secondary flywheel 3.

It is further desirable to install the externally threaded shanks of thefasteners 8 in the respective holes 7 during assembly of theaforementioned unit including the parts 2, 3, 4 (with 5) and 6. Thisresults in further shortening of the interval which is needed toseparably affix the primary flywheel 2 to the output element of anengine. Each of the fasteners 8 can constitute a so-called hexagonsocket screw or bolt, i.e., a bolt having a head 33 with a polygonalsocket for the working end of a tool which is used to drive the shank ofa fastener 8 into the adjacent tapped bore or hole in the output elementof the engine. The fasteners 8 can be securely held in their holes 7 byresorting to elastic securing means, preferably securing means of thetype to be destroyed or to yield when the working end of theaforementioned tool is introduced into the socket of the respective head33. Thus, the securing means must or should be designed to preventseparation of the fasteners 8 from the primary flywheel 2 prior toattachment of such flywheel to a crankshaft or another suitable outputelement of an engine. Reference may be had to the aforementionedcommonly owned U.S. Pat. No. 5,160,007 to Reik et al. which fullydescribes and shows suitable securing means as well as a tool which canbe used to drive the fasteners for the primary flywheel home byovercoming the resistance of (e.g., by destroying or by pushing aside)the securing means.

The flange 5c of the clutch disc 5 has holes 32 (e.g., at leastsubstantially circular openings or slots having an oval or a polygonaloutline) which are in at least partial alignment with the holes 7 in thepreassembled unit including the flywheels 2, 3, the clutch 4, thebearing 6 and the fasteners 8. This ensures that the working end of theaforementioned torque transmitting tool can be inserted into the socketsof the heads 33. As already mentioned above, the clutch disc 5 iscentered between the friction surface 3a of the secondary flywheel 3 andthe pressure plate 31 of the friction clutch 4 during the making of theaforementioned preassembled unit so that the axis of the clutch disc 5automatically coincides with the axis of the output element of theengine when such output element is properly connected with the primaryflywheel 2. The cross-sectional area of each hole 32 can be smaller thanthe cross-sectional area of the head 33 of a fastener 8; this alsoensures that the fasteners 8 cannot be lost or misplaced once theassembly of the aforementioned unit is completed; at the same time, suchrelatively small holes 32 still permit the introduction of the workingend of a torque transmitting tool into the preferably hexagonal socketin a selected head 33 in order to drive the shank of the respectivefastener 8 into the adjacent tapped bore or hole in the output elementof the engine.

The diaphragm spring 34 of the friction clutch 4 is also provided withholes 35 or analogous passages for the torque transmitting tool, andsuch holes or passages are aligned with the holes 32 of the clutch disc5 as well as with the holes 7 in the primary flywheel 3, at least to anextent which is necessary to permit entry of the working end of a torquetransmitting tool into the socket of any one of the heads 33. The holesor passages 35 can constitute enlarged portions of slots between certainpairs of neighboring substantially radially extending prongs or tongues34a of the diaphragm spring 34.

Additional holes or passages 36 are provided in the radially innerportion of the secondary flywheel 3, and each hole 36 is in at leastpartial alignment with a hole or passage 35, a hole 32 and a hole 7,namely in an alignment which is needed to permit introduction of thetorque transmitting tool into the socket of a selected head 33.

The friction clutch 4 of FIG. 1 is a so-called push-type clutch, i.e,the radially inner portions of prongs 34a forming part of the diaphragmspring 34 must be depressed (e.g., by a suitable bearing or anotherdepressing means) in order to tilt the diaphragm spring relative to thecover 30 to an extent which is necessary to permit disengagement of thepressure plate 31 from the adjacent lining 5a of the clutch disc 5 andto thus interrupt the transmission of torque from the secondary flywheel3 to the input element of the variable speed transmission carrying thehub 5b. The diaphragm spring 34 automatically returns the pressure plate31 into requisite engagement with the adjacent friction lining 5a assoon as the force acting upon the free end portions of the prongs 34a isterminated or relaxed so that the diaphragm spring can reassume thecondition which is shown in FIG. 1.

However, the present invention can be embodied with equal or similaradvantage in a torque transmitting apparatus employing a so-calledpull-type friction clutch, namely a clutch wherein the prongs of thediaphragm spring must be pulled in a direction away from the pressureplate in order to disengage the friction clutch. between two ring-spacedseats 37, 38 which can be made of metallic wire or the like. The seat 37is immediately adjacent the inner side of a radially extending secondportion or section 30a of the clutch cover 30, the circumferentiallycomplete main portion of the diaphragm spring 34 is disposed between theseats 37, 38 and these seats are held in requisite positions on thesection 30a by a set of rivets 40 (only one shown in FIG. 1). The rivets40 further carry portions of leaf springs 39 which serve to affix thepressure plate 31 to the cover 30 in such a way that the pressure plateis held against rotation relative to the parts 3 and 30 but is free tomove (within limits) axially of the composite flywheel assembly 1 whenthe friction clutch 4 is disengaged. Several discrete leaf springs 39can be replaced with a single resilient element which is designed toensure that the pressure plate 31 rotates with the cover 30 andsecondary flywheel 3 but is free to perform limited axial movements whenthe clutch 4 is disengaged. Furthermore, the leaf springs 39 (or theaforementioned one-piece substitute for such springs) can perform (andnormally does perform) the additional function of automaticallydisengaging the left-hand (friction) surface of the pressure plate 31from the adjacent friction lining 5a when the clutch 4 is disengaged,i.e., when the pressure plate 31 is free to move away from and in theaxial direction of the secondary flywheel 3.

As can be seen in FIG. 1, one end portion of each leaf spring 39 isaffixed to the section 30a of the clutch cover 30 by a rivet 40, and theother end portion of each leaf spring 39 is affixed to a radiallyinwardly extending arm 31a of the pressure plate 31 by a rivet 41. Therivets 41 can be replaced with rivet-shaped integral portions of thepressure plate 31; the connections between the leaf springs 39 and thepressure plate are then shifted (or can be shifted) radially outwardlyto be aligned with portions of the right-hand friction lining 5a.Furthermore, radially outward shifting of connections between the leafsprings 39 and the pressure plate 31 can also take place if the rivets41 are replaced with blind rivets. Such modified connection between thepressure plate 31 and the leaf springs 39 (or a one-piece substitute forthe leaf springs 39) can be used with particular advantage if thepressure plate 31 is a forging or stamping. The necessary space(occupied by the projections 42 of the pressure plate 31 shown inFIG. 1) for engagement between the pressure plate and the main portionof the diaphragm spring 34 can be taken up by such projections 42 or,alternatively, by a preferably circular ring-shaped insert (not shown)which is partially recessed into a circumferentially extending groove(not shown) in the right-hand side or surface of the pressure plate. Theinsert can be a press fit or it can be otherwise secured in the grooveof the pressure plate 31. If the illustrated push-type friction clutch 4is replaced with a pull-type friction clutch, those end portions of theleaf springs 39 which are affixed to the pressure plate 31 arepreferably located radially outwardly of the rivets 40 and/or the mainportion of the diaphragm spring 34. Moreover, it is then possible ornecessary to provide discrete rivets or other suitable connectors (inaddition to the rivets 40) in order to secure one end portion of eachleaf spring 39 to the clutch cover 30.

The holes 36 in the secondary flywheel 3 and the holes 32 in the flange5c of the clutch disc 5 further serve to permit and/or induce thecirculation of air to thus maintain the improved apparatus at anacceptable temperature. Additional ventilating holes or passages 43 areprovided in the clutch cover 30, and the secondary flywheel 3 is alsoprovided with ventilating holes or passages 44 and 45. Adequate coolingof the entire apparatus exhibits a number of important advantages; forexample, the paste-like lubricant which fills at least a portion of thechamber 11 (particularly the compartment 12) is less likely to be heatedto a temperature at which its viscosity is greatly reduced so that atleast some of the lubricant would be likely to escape from the chamber11 by flowing past the sealing device 24 and/or 25. Moreover,overheating would be likely to shorten the useful life of the apparatus.

The apparatus can be further provided with a pilot bearing (not shown)which is to be installed in the primary flywheel 2 to enter a socket inthe output element of the engine. For example, the pilot bearing can beinstalled in the radially inner portion of the tubular carrier 15. Stillfurther the damper 9 can be used in conjunction with, or it can bereplaced by, one or more different dampers and/or by one or morefriction generating devices (not shown) which are effective during eachand every stage or during certain stages of angular movement of theflywheels 2, 3 relative to each other. If two or more frictiongenerating devices are to be employed, they may but need not be ofidentical design. A pilot bearing is shown, for example, in FIG. 2 ofthe aforementioned commonly owned U.S. Pat. No. 5,160,007 to Reik et al.Friction generating devices are shown, for example, in commonly ownedU.S. Pat. No. 5,146,811 granted Sep. 15, 1992 to Jackel for "Vibrationdamping apparatus".

The tubular section 29 of the composite clutch cover 30 is provided withrecesses 49 and 51 (FIG. 2) which are formed therein in accordance withthe method of the present invention. This tubular section is fixedlysecured to and thus shares all movements of the secondary flywheel 3; inaddition, the section 29 is connected with the radially extendingsection 30a of the cover 30 by a set 46 of threaded connecting elementsor fasteners 48 at least some of which extend into the recesses 49and/or 51, all as will be described in greater detail hereinafter. Thesection 29 can constitute a treated metallic workpiece in the form of athin-walled cylinder with the recesses 49, 51 provided in that end faceor surface 50a (FIGS. 2 to 4) of the cylinder which is adjacent theradially outer part of the section 30a. The latter is provided withsubstantially flange-like radially outwardly extending portions 47 eachof which is secured to the adjacent axial end 50 of the section 29 by atleast one threaded fastener 48. The axes of the fasteners 48 are atleast substantially parallel to the axis of the composite flywheelassembly 1. The heads of properly applied fasteners 48 bear against theouter sides of the respective flange-like portions 47 and the shanks ofsuch fasteners extend into the tapped recesses 49 of the adjacent axialend 50 of the section 29. The recesses 51 (also provided in the endsurface 50a of the axial end 50) are not tapped and alternate with thetapped recesses 49 in the circumferential direction of the section 29.The arrangement may be such that individual recesses 51 alternate withsets of two or more recesses 49, that individual recesses 49 alternatewith sets of two or more recesses 51 and/or that sets of two or morerecesses 49 alternate with sets of two or more recesses 51.

The method of making the tapped recesses 49 will be described in detailwith reference to FIGS. 2, 3 and 4. FIG. 2 shows the end surface 50a ofthe axial end 50 forming part of the section 29. The surface 50a isfurther provided with the untapped recesses 51 which serve to receive,for example, locating and/or centering pins having portions extendingfrom the recesses 51 and into aligned recesses (e.g., through holes) inthe flange-like portions 47 (and/or other portions) of the section 30a.The pins facilitate accurate centering of the sections 29 and 30arelative to each other during assembly of the composite clutch cover 30.

The wall thickness of the section 29 is changed in the regions of therecesses 49 and 51; the wall thickness of all other portions of thesection 29 is or can be unchanged. As can be seen in FIG. 2, thediameter of a recess 49 or 51 exceeds the wall thickness of undeformed(non-recessed) portions of the section 29. The deformed portions of thesection 29 immediately surround the respective recesses 49 and 51.

The wall thickness of the section 29 need not be constant from end toend, i.e., in the axial direction of such section. This can be seen inFIG. 3 which shows that the wall thickness of the left-hand axial end isless than that of the right-hand axial end portion 50. FIG. 3 furthershows that, save for its deepmost portion, the diameter of the recess 49which is shown therein can be constant and can exceed the original wallthickness of the respective portion of the section 29. For example, theoriganal wall thickness of a portion which has been provided with arecess 49 or 51 can amount to approximately 90 percent of the diameterof the respective recess. The diameter of that portion of a centering orlocating pin which is received in a recess 51 can exactly match or atleast very closely approximate the diameter of the respective recess 51,i.e., it can also exceed the original wall thickness of that portion ofthe section 29 which is provided with a recess 51.

The recesses (such as 49 and/or 51) need not be provided only in thesurface 50a; such recesses or similar recesses can also be formed in theother end face or surface 50b of the section 29. FIG. 3 shows that thesurface 50b is provided with a recess in the form of a slot 52 extendingfrom the surface 50b toward but well short of the surface 50a. Thetongue-like portions or arms 52a between the slots 52 can serve toreceive torque from the support 22 of arms 21 (see FIG. 1), i.e., torotate the entire cover 34 in response to rotation of the secondaryflywheel 3 (which mounts the support 22 and its arms 21). If the support22 is omitted, the arms 52a between the recesses or slots 52 in thesurface 50b of the section 29 can serve to directly engage the endportions of the adjacent coil springs 10, i.e., to constitute componentparts of the damper 9. Still further, and if the support 22 and its arms21 are omitted, the arms 52a between the recesses or slots 52 can serveto receive torque from the secondary flywheel 3, i.e., to rotate thecover 30, the diaphragm spring 34 and the pressure plate 31 in responseto rotation of the flywheel 3.

It is further possible to provide additional recesses (e.g., in the formof slots resembling the slots 52) in the surface 50a of the section 29,e.g., so that such slots alternate with the recesses 49 and 51. Theslots in the surface 50a can be used to establish paths for the flow ofair which cools the torque transmitting apparatus in actual use.

In accordance with a presently preferred embodiment of the improvedmethod, the section 29 of the composite cover 30 can be produced andtreated in the following way: One starts with a first blank which ismade of sheet metal and can constitute a flat plate or a coil. The plateor coil is trimmed or subdivided to constitute or to yield at least onesecond blank, e.g., a circular piece of a polygonal or oval piece ofmetallic sheet material. The second blank is thereupon shaped in astamping or other suitable machine to be converted into a cupped bodyhaving an axially extending cylindrical or sleeve-like portion and aradially extending disc-shaped portion at one axial end of thecylindrical portion. The conversion of a second blank (e.g., a flatcircular disc) into a cupped body can be effected by deep drawing, i.e.,a technique which involves deformation of the second blank as a resultof forming involving the combined application of tensile and compressivestresses. The thickness of the radially extending disc-shaped portion ofthe cupped body matches or at least approximates the thickness of thesecond blank. On the other hand, the thickness of the cylindricalsleeve-like portion of the cupped body exceeds the thickness of thesecond blank; this is due to the aforedescribed method (deep drawing) ofconverting the second blank into a cupped body; such deep drawinginvolves upsetting the part which is to constitute the sleeve-likeportion. The sleeve-like portion of the cupped body serves for themaking of the section 29, and the radially extending portion of thecupped body serves for the making of the section 30a of a finishedclutch cover 30. The plastic deformation of second blank during deepdrawing involves a flow of the metallic material to form the cylindricalsleeve-like portion; this is desirable and advantageous because thematerial of the sleeve-like portion is densified with attendant increaseof stability.

Deep drawing constitutes but one of the procedures which can be reliedupon in order to form a cupped body which is ready to be converted intoa clutch cover 30. For example, it is possible to form the cupped bodysolely as a result of the application of pressure (e.g., in anextruder). Irrespective of the selected mode of converting a plate ordisc (second blank) into a cupped body, it is advisable to resort tocold forming because this results in an increase of hardness of thematerial of the cupped body.

The just discussed making of the cupped body is preferably followed by aso-called ironing step which involves a reduction of the thickness ofthe cylindrical sleeve-like portion to a preferred thickness of thesection 29. As already mentioned above, the wall thickness of thesection 29 need not be constant, i.e., the ironing step need not involvea reduction of the thickness to a value which is the same in each andevery zone of the sleeve-like portion of the cupped body. In manyinstances, the thickness of the section 29 will vary in a direction fromthe surface 50a toward the surface 50b, i.e., in the axial direction.

The ironing step renders it possible to select the dimensions of thesleeve-like portion (and hence of the section 29) with a high degree ofaccuracy which often suffices so that the sleeve-like portion and/or thesection 29 need not be subjected to any additional calibratingtreatment. In addition to involving a desirable calibration of thesleeve-like portion of the cupped body, the ironing step is desirable onthe ground that it further enhances certain desirable qualities (such ashardness) of the section 29.

The ironing step is followed by a severing step which involvesseparation of the cylindrical sleeve-like portion from the radiallyextending portion of the cupped body. If necessary, the external and/orthe internal surface of the separated cylindrical sleeve-like portioncan be subjected to a calibrating treatment; such treatment can involvecalibration of a portion of or of the entire internal and/or externalsurface of the separated or severed sleeve-like portion. It is to benoted, again, that the aforediscussed ironing of the cylindricalsleeve-like section prior to severing of the cupped body often sufficesto ensure adequate calibration of the section 29, i.e., calibrating ofthe internal and/or external surface of the sleeve-like portionsubsequent to severing of the cupped body is optional and can bedispensed with in many instances.

The next step involves the making of recesses 49, 51 in the surface 50aof axial end 50 of the section 29 (i.e., of the separated cylindricalsleeve-like portion of the cupped body). To this end, the section(workpiece) 29 is clamped between two work holders 53, 54 (FIGS. 2 and3) in such a way that the work holders provide room for radial expansionof those selected portions of the axial end 50 which are to be providedwith the recesses 49 and 51. The outer work holder 53 has a concaveinternal surface with sockets 55 which permit the material of thesection 29 to flow transversely of the axes of the recesses 49 and 51.Each socket 55 is in register with a socket 56 in the convex externalsurface of the other work holder 54 which is surrounded by the section29. FIG. 3 shows that the sockets 55 and 56 need not extend all the waybetween the surfaces 50a and 50b but only to an extent which isnecessary to take into consideration the desired axial length (depth) ofthe recesses 49 and 51 each of which constitutes a blind hole.

FIG. 3 shows a portion of an elongated piercing or material displacingtool 57 in the form of a pin or post having a trailing portion 59a and afront portion or leader 59. The cross-sectional area of the trailingportion 59a is greater than that of the leader 59. The illustratedleader 59 constitutes a cone or a pyramid whose cross-sectional areadecreases gradually in a direction (arrow 58) away from the trailingportion 59a. The tool 57 is driven into the surface 50a to a desiredextent, i.e., to form a recess 49 or 51 of desired depth or axiallength. The direction which is indicated by the arrow 58 is parallel tothe axis of the section 29. Penetration of the leader 59 into thesurface 50a takes place while the holders 53 and 54 clamp the workpiece(section 29) against any stray movements which could affect the accuracyof the positioning and/or orientation and/or dimensions of a recess 49or 51. As the leader 59 (and thereupon the immediately followingportion) of the tool 57 penetrates into the surface 50a, the metallicmaterial of the section 29 is displaced radially outwardly into theadjacent sockets 55 and 56, i.e., transversely of the direction which isindicated by the arrow 58. The means (e.g., a hammer, a piston, a ram orany other suitable device) for driving the tool 57 into the surface 50ais not shown in the drawing. Such driving means can be caused to bear orto (if necessary repeatedly) strike against the enlarged trailingportion 59a of the tool 57. The illustrated trailing portion 59a isoptional, i.e., the diameter of the tool 57 can be constant all the wayfrom the rear end of the leader 59 to the rearmost end of the tool.

The illustrated tool 57 can constitute a centering or locating pin,i.e., it can remain in a recess 51 and that portion of the tool 57 whichextends from a recess 51 then serves as a means for centering thesections 29 and 30a of an assembled cover 30 relative to each other.

Since the recesses 49 are provided with internal threads, it isnecessary to extract a tool 57 which was used to form such recesses bypulling the tool in a direction counter to that indicated by the arrow58, and the thus obtained recess (51) is converted into a tapped blindhole (49) by resorting to a suitable additional tool, e.g., a tool whichcan provide the surfaces surrounding the partially finished recesses 49(each such partially finished recess can be said to constitute a recess51) with a suitable internal thread without removing material from thesection 29. The thread cutting tool can remain in the thus obtained(finished) recess 49, e.g., to receive one or more nuts or otherinternally threaded fasteners. For example, the internal thread can beformed with a sheet metal screw or such screw (note the fastener 48 inFIG. 1) can be driven into a recess 49 when the tapping operation iscompleted. The utilization of tapping tools which can provide thesurfaces surrounding the recesses 51 with threads (to convert suchrecesses 51 into recesses 49) is preferred at this time because thematerial of the section 29 is not wasted and the machine in which thesections 29 are treated is not contaminated with fragments of removedmetallic material. The tapping tools can receive nuts (to fix thesection 29 to the section 30a) if such tools are not screws. If thetapping tools are not screws but the sections 29 and 30a are to besecured to each other by screw-like fasteners (such as 48), the tappingtools are removed from the freshly formed recesses 49 to be replacedwith screws or bolts.

The material displacing tool 57 of FIG. 3 is but one example of a largevariety of tools which can be utilized for the practice of the improvedmethod. For example, the tool can have an oval, polygonal or othersuitable cross-sectional outline departing from a circular outline.Furthermore, the leader of the tool need not be a cone or a pyramid aslong as it is designed in such a way that its cross-sectional area issmaller than that of the (trailing) portion behind it. Still further,all of the recesses 51 or all of the recesses 49 need not be formed byresorting to one and the same material displacing tool or to a set ofidentical tools. For example, the surface 50a can be provided with anarray of recesses 51 having different cross-sectional outlines,different depths and/or both, and the same holds true for the toolswhich are to be used to make the tapped recesses 49. Two or morematerial displacing tools can be applied simultaneously; for example,all of the recesses 51 can be made in a single step, all of the(untapped) recesses 49 can be made in a single step, and all of thestill untapped recesses 49 can be tapped simultaneously.

It is further within the purview of the invention to employ one or moretools which are designed to provide a surface (such as the surface 50a)with one or more arcuate recesses. For example, and as shown in FIG. 5,a material displacing tool 257 can constitute a cylinder including aring-shaped leader 259 and a trailing portion 259a having a largercross-sectional area than the leader 259. The width of a recess which isobtained with the tool 259 can match the original wall thickness of aworkpiece, such as the section 29 of FIGS. 1 to 4. The circumferentiallycomplete recess which can be formed with the tool 257 can be replacedwith an interrupted recess having two or more arcuate sections; this canbe accomplished by using a tool which constitutes a modification of thetool 257, namely a tool having suitably distributed slots in the leader259.

If the material of a workpiece which is to be provided with one or morerecesses in accordance with the method of the present invention exhibitsat least some resiliency, the material displacing tool can be designedin such a way that it permits some of the displaced metallic material toflow back radially inwardly toward the center of the recess. The tool157 of FIG. 4 has circumferentially extending grooves 157a which arefilled with the material of the workpiece 29 to ensure that the properlydriven tool can be reliably held in the thus obtained recess. Thediscrete circumferentially extending grooves 157a can be replaced withone or more helical groves or with any other undercuts which enable thedisplaced material to flow back toward the axis of the recess and tothus anchor the material displacing tool in the recess. A materialdisplacing tool of the type shown at 157 can be used for the making ofrecesses 49 and/or 51.

Any additional recesses which are to be provided in the section 29 ofFIGS. 2, 3 and 4 can be formed in the surface 50a prior or subsequent tothe making of recesses 49 and/or 51. The additional recesses canconstitute slots (such as the slot 52 shown in FIG. 3), blind holes withor without threads therein and/or others. For example, recesses in theform of slots can be provided in the surface 50a simultaneously with thesevering of a cupped body into two discrete parts one of which is toconstitute the section 29 and the other of which is to constitute thesection 30a of a clutch cover 30.

An important advantage of the improved method is that it renders itpossible to provide one or more recesses by the simple expedient ofdisplacing, rather than removing, some material of the workpiece. Thematerial displacing tool exhibits the advantage that it is simple andinexpensive as well as that it can be left (at least under certaincircumstances, i.e, for certain uses of the treated workpiece) in afreshly formed recess to thereupon form part of the treated workpieceand/or of the apparatus, device, machine or implement in which theworkpiece is to be put to use. Furthermore, the improved method and thematerial displacing tool for the practice of such method exhibit theadvantage that one or more recesses can be formed in a thin-walledworkpiece, such as the section 29, and that the recess or recesses canextend in parallelism with the axis of a tubular or cylindricalworkpiece.

Still another advantage of the improved method and of the materialdisplacing tool is that the workpiece can be provided with one or morerecesses having maximum transverse dimensions at least matching (but, ifnecessary, even greatly exceeding) the wall thickness of the workpieceprior to making of one or more recesses therein. The ratio of theinitial wall thickness to the maximum transverse dimension of a recesscan be in the range of 0.5 to 2, preferably 0.7 to 1.5. If a recess hasa circular cross-sectional outline, its maximum transverse dimensionmatches the diameter, and such diameter can considerably exceed thethickness of a workpiece (such as a cover section 29) prior to themaking of one or more recesses therein. However, and as alreadymentioned above, a recess which has been formed in accordance with theimproved method can have an oval, polygonal or other non-circularcross-sectional outline.

The work holders 53, 54 of FIGS. 2 and 3 (or other suitable workholders) exhibit the advantage that they do not interfere with the flowof metallic material (transversely of the direction which is indicatedby the arrow 58) during penetration of the leader 59 and of thenext-following portion of a tool 57 into the surface 50a. Such designand mode of utilizing the work holders ensure that the material of theworkpiece does not undergo any unnecessary or undesirable densificationaround a recess 49 or 51 during, or as a result of, penetration of thematerial removing tool 57 or another suitable tool into the surface 50a.

A hollow workpiece in the form of a tube or cylinder (such as thesection 29 of the clutch cover 30) constitutes one of the presentlypreferred workpieces to be treated in accordance with the improvedmethod. The workpiece is preferably treated in a drawing machine priorto the making of one or more recesses therein. Such treatment isdescribed, for example, in commonly owned German patent applicationSerial No. P 41 32 421.8, which corresponds to U.S. application Ser. No.07/952,582, now U.S. Pat. No. 5,257,715. The aforedescribed ironingoperation prior to the making of one or more recesses in the workpieceexhibits the advantage that the workpiece need not be subjected (or neednot always be subjected) to an additional or separate calibrating stepwhen the ironing step is completed. This saves time and equipment andcontributes to lower cost of the treated workpiece as well as of theentire apparatus in which the treated workpiece (with one or morerecesses therein) is being put to use. In many instances, somecalibrating of a portion of the external and/or internal surface of theworkpiece prior to making of one or more recesses therein suffices evenif the workpiece must be finished (e.g., converted into the tubular orcylindrical section of a clutch cover) with an externally high degree ofprecision.

The surface (such as the surface 50a of the section 29) to be providedwith a recess can extend at right angles to the axis of the workpiece,and the axis of each of the recesses 49, 51 is or can be at leastsubstantially parallel to such axis.

The method can be practiced by resorting to a single material displacingtool (such as 57) if a surface of a workpiece is to be provided with asingle recess or with two or more identical recesses. The single toolmust be withdrawn upon completion of the making of each preceding recessbut can be left in the last one of a series of two or more recesses.Alternatively, the method can be practiced with a plurality of materialdisplacing tools which can be driven into selected portions of a surfaceon a workpiece, either one after the other, in groups of two or more, orall at the same time, and thereupon remain in the respective recesses,e.g., to constitute the aforementioned centering and/or locating postsor pins which ensure reliable and predictable as well as highly accuratecentering of the treated workpiece relative to an associated workpiece,e.g., of the section 29 relative to the section 30a of the clutch cover30 which is shown in FIG. 1.

If the recess or recesses are to constitute tapped blind holes orthrough holes, it is often advisable to leave the tapping tools in therespective tapped holes. This ensures that the tools are received in therespective tapped holes with no play at all and can be utilized tocenter the finished workpiece relative to one or more additional partswith an extremely high degree of accuracy. This is often necessary inthe friction clutch of a motor vehicle. Each of the thus anchoredexternally threaded tapping tools can be caused to mesh with one or morenuts or other internally threaded fasteners. Alternatively, each of thethus anchored externally threaded tools can be provided with an integralhead which serves as a means for holding one or more additional parts inrequisite position or positions related to the finished workpiece havingone or more tapped holes with the tapping tool or tools remainingtherein. Each tapping tool can be driven home in the respective tappedhole with a considerable force to reduce the likelihood of loosening inactual use of the apparatus which employs the finished workpiece.

If the workpiece is provided with one or more recesses in the form ofuntapped holes, each such recess can receive (preferably with minimalclearance or with no clearance at all) the smooth portion of a locating,centering or other pin, and each such pin can have an externallythreaded portion outside of the respective untapped hole to accept oneor more nuts or other female (internally threaded) fasteners.

Reliable anchoring of a locating or centering pin in an untapped recess(such as 51) can be ensured by positively displacing some of thepreviously displaced metallic material against the inserted portion ofsuch pin. In other words, if the original material displacing tool is tobe withdrawn from a freshly formed recess 51, it is replaced by thesmooth portion of a centering pin and the material which has beendisplaced by the original material displacing tool is thereupon causedor permitted to move back toward its original position in order toreliably confine the smooth portion of the centering or locating pin inits recess. The arrangement is preferably such that a cylindricalcentering or locating pin is reliably installed against any movement inthe radial, axial and/or circumferential direction of the respectiverecess 51.

It has been found that the improved method can be resorted to withparticular advantage for the treatment of workpieces which are toconstitute component parts or constituents of friction clutches for usein motor vehicles or in torque transmitting apparatus, e.g., inapparatus of the type shown in FIG. 1. Such workpieces can be treated inaccordance with the entire aforedescribed method (i.e., including themaking of a first blank, converting the first blank into a second blank,converting the second blank into a cup-shaped body, cutting up the bodyto form two sections, ironing and/or otherwise calibrating the tubularsection and providing the thus treated tubular section with one or morerecesses in the end surface 50a, 50b and/or elsewhere. The thus treatedtubular section 29 is then ready to be assembled with the section 30a toform therewith a clutch cover 30.

A workpiece which has been treated in accordance with the method of thepresent invention can be utilized with particular advantage incombination with a composite flywheel assembly, such as that includingthe flywheels 2, 3 shown in FIG. 1 and also described and shown incommonly owned published German patent application Serial No. P 40 27629.5, which corresponds to U.S. application Ser. No. 07/708,935, nowU.S. Pat. No. 5,261,516 and in the aforementioned commonly owned U.S.Pat. No. 5,160,007 to Reik et al. Thus, a workpiece having one or morerecesses formed in accordance with the novel method can be mounted onthe secondary flywheel to constitute a component part of a clutch cover.The section 29 of the cover 30 can be provided with a single set ofrecesses 51 (without threads), with a single set of recesses 49 in theform of tapped blind holes, or with a combination of tapped and untappedholes, depending on the nature of connection between the sections 29 and30a. The section 30a will be separated from the section 29a in order toafford access to the diaphragm spring 34, to the pressure plate 31, tothe leaf springs 39 and/or to any other parts which are not accessiblewhile the section 30a is affixed to the section 29. Inspection, repairor replacement of the clutch disc 5 (or another clutch disc which isused in lieu of the clutch disc 5) also necessitates separation of thesection 30a from the section 29. It has been found that the utilizationof a set of threaded fasteners (such as 48) constitutes a very simpleand highly satisfactory solution of the problem of affording convenientaccess to certain component parts of the friction clutch 4, namely tothose parts which become accessible only upon detachment of the section30a from the section 29.

Once the section 30a is separated from the section 29, it can be movedaway from the secondary flywheel 3 together with the pressure plate 31,leaf springs 39, seats 37, 38 and diaphragm spring 34. This renders itpossible to inspect and (if necessary) replace the parts 31, 34, 37, 38,39 as well as to afford convenient access to the clutch disc 5.

Separation of the section 29 from the secondary flywheel 3 involveswithdrawal of the aforementioned portions 52a between the slots 52 inthe end surface 50b of the section 29 from the carrier 22, and theportions 52a are automatically reengaged with the support 22 when thesection 29 is reattached to the secondary flywheel. All of theaforedescribed features simplify the assembly and dismantling of thefriction clutch 4 and of the entire torque transmitting apparatus andrender it possible to replace or inspect any of the parts which are notreadily accessible in conventional friction clutches and torquetransmitting apparatus. The portions 52a between the slots 52 can be ofone piece with the section 29 or they can constitute separately producedparts which are welded, soldered or otherwise (directly or evenindirectly) affixed to the section 29.

The method of the present invention can be practiced with particularadvantage in connection with the treatment of workpieces which are toconstitute component parts of composite covers or housings for frictionclutches. As already described with reference to the drawings, theimproved method can be resorted to with advantage for the treatment ofthe axially extending section 29 of a composite clutch cover, namely toprovide the section 29 with one or more recesses in the form of tappedor untapped blind or through holes which can extend in parallelism withthe axis of the section 29. However, it is equally possible to practicethe improved method in connection with the making of recesses havingaxes which are inclined with reference to the axis of the workpiece. Ithas been found that the assembly of modules (such as the aforediscussedpreassembled unit including the composite flywheel assembly 1, thebearing 6 and the friction clutch 4 including the clutch disc 5) can besimplified and the cost of such assembly reduced if at least oneconstituent of the assembly is treated in accordance with the method ofthe present invention. Such treatment can involve the making of one ormore recesses exclusively in accordance with the improved method or themaking of one or more recesses in accordance with the improved methodand the making of one or more recesses by resorting to suitable materialremoving (rather than material displacing) tools or the like.

The improved method and the apparatus or parts thereof which areproduced and/or treated in accordance with such method can be modifiedin a number of additional ways without departing from the spirit of theinvention. For example, the method can be practiced to make recesses(e.g., blind holes and/or through holes with or without threads) inother components of a torque transmitting apparatus. Furthermore, themethod can be practiced for the making of recesses in metallic partsother than those which are to be assembled into a torque transmittingapparatus, a friction clutch or another device destined for use in amotor vehicle.

Without further analysis, the foregoing will so fully reveal the gist ofthe present invention that others can, by applying current knowledge,readily adapt it for various applications without omitting featuresthat, from the standpoint of prior art, fairly constitute essentialcharacteristics of the generic and specific aspects of our contributionto the art and, therefore, such adaptations should and are intended tobe comprehended within the meaning and range of equivalence of theappended claims.

We claim:
 1. A metallic component constituting an element of a frictionclutch and having a tubular section which has an internal surface, anexternal surface and an axial end surface between said internal andexternal surfaces, said end surface being provided with at least onerecess which is formed as a result of driving into the end surface amaterial displacing tool, said tool including a trailing portion havinga larger first cross-sectional area and a leader having a smaller secondcross-sectional area and having been driven into the end surface in sucha way that the leader has penetrated the end surface in a direction fromthe trailing portion toward the leader and the tool has displaced thematerial of the metallic component at least substantially transverselyof said direction.
 2. The component of claim 1, comprising a housingincluding said tubular section and a second section detachably connectedto the tubular section.
 3. A friction clutch comprising a compositeflywheel assembly connectable to a combustion engine and including asecondary flywheel; a tubular metallic component carried by saidsecondary flywheel and having a tubular section which has an internalsurface, an external surface and an axial end surface between saidinternal and external surfaces, said axial, end surface being providedwith a plurality of tapped recesses spaced apart from each othercircumferentially of said tubular component, at least one of saidrecesses being formed as a result of driving into said end surface amaterial displacing tool, said tool including a trailing portion havinga larger first cross-sectional area and a leader having a smaller secondcross-sectional area and having been driven into said end surface insuch a way that the leader has penetrated the end surface in a directionfrom said trailing portion toward the leader and the tool has displacedthe material of the metallic component at least substantiallytransversely of said direction; a clutch housing section adjacent saidend surface; and threaded fasteners securing said housing section tosaid component and having portions extending into said recesses.
 4. Thefriction clutch of claim 3, wherein said housing section extendssubstantially radially of and is detachably connected to said tubularcomponent, and further comprising a diaphragm spring tiltably carried bysaid housing section.
 5. The friction clutch of claim 3, wherein saidsecondary flywheel is rotatable about a predetermined axis and furthercomprising a pressure plate and means for non-rotatably securing saidpressure plate to said tubular component for movement in the directionof said axis.
 6. The friction clutch of claim 3, further comprisingenergy storing elements deformable in the circumferential direction ofsaid composite flywheel, said tubular component having means fordeforming said energy storing elements.
 7. A torque transmittingapparatus, comprising a composite housing rotatable about apredetermined axis, said housing including a component having a tubularsection extending in the direction of said axis and having an internalsurface, an external surface and an axial end surface disposed betweensaid internal and external surfaces and provided with at least onerecess which is formed as a result of driving into the end surface amaterial displacing tool, said tool including a trailing portion havinga larger first cross-sectional area and a leader having a smaller secondcross-sectional area and having been driven into said end surface insuch a way that the leader has penetrated the end surface in a seconddirection from said trailing portion toward said leader and the tool hasdisplaced the material of the component at least substantiallytransversely of said second direction.
 8. The apparatus of claim 7,wherein said housing constitutes a cover of a friction clutch for use inmotor vehicles.
 9. Apparatus for compensating for torsional stresses,comprising a first flywheel connectable with an engine; a secondflywheel connectable with an input element of a transmission, saidflywheels being rotatable relative to each other; at least one damperhaving means for yieldably opposing rotation of said flywheels relativeto each other, at least one antifriction bearing interposed between saidflywheels; a metallic component having a tubular section affixed to oneof said flywheels and extending in the direction of the axis of rotationof said one flywheel, said component having an internal surface, anexternal surface and an axial end surface disposed between said internaland external surfaces and having at least one recess formed as a resultof driving into the end surface a material displacing tool, said toolincluding a trailing portion having a larger first cross-sectional areaand a leader having a smaller second cross-sectional area and havingbeen driven into said end surface in such a way that the leader haspenetrated the end surface in a second direction from said trailingportion toward said leader and the tool has displaced the material ofthe component at least substantially transversely of said seconddirection; and a cover portion connectable to said component.
 10. Theapparatus of claim 9, further comprising means for affixing one of saidflywheels to an output element of a combustion engine.
 11. A frictionclutch comprising a sheet metal housing including an at leastsubstantially cylindrical first section having an axial end and a secondsection disposed at said axial end and extending at least substantiallyradially of said first section; threaded fasteners detachably connectingsaid sections to each other; a pressure plate non-rotatably affixed tosaid housing for movement in the axial direction of said first section;and means for biasing said pressure plate axially of said first section,said axial end having an internal surface, an external surface and anend surface disposed between said internal and external surfaces andprovided with recesses extending substantially axially of said firstsection and formed as a result of driving into said end surface amaterial displacing tool which has displaced the material of said firstsection substantially radially of the respective recess.
 12. A frictionclutch comprising a component including a substantially cylindricalsection; a composite flywheel assembly including a flywheel connectablewith an output element of a combustion engine; energy storing elementsacting in the circumferential direction of and reacting against saidassembly; and torque transmitting elements provided on saidsubstantially cylindrical section and bearing against said energystoring elements, said component further comprising a second sectiondetachably connected to said substantially cylindrical section, saidsubstantially cylindrical section consisting at least in part of ametallic sheet material and having an internal surface, an externalsurface and an end surface disposed between said internal and externalsurfaces adjacent said second section and being provided with recessesat least one of which is formed as a result of displacing the materialof said substantially cylindrical section substantially radially of anaxis of the at least one recess.
 13. A metallic component constitutingan element of a friction clutch and having an axially extending tubularsection which consists of sheet metal, said tubular section having anaxial cross-section which is longer in an axial dimension than in aradial dimension and which has an axial end surface, said end surfacebeing provided with at least one recess for receiving a fastener forconnecting a housing to said friction clutch, said at least one recessbeing formed as a result of displacement of said sheet metal andextending in said sheet metal in an axial direction of said tubularsection.
 14. A friction clutch comprising a composite flywheel assemblyconnectable to a combustion engine and including a secondary flywheel; atubular metallic component carried by said secondary flywheel and havingan axially extending tubular section which consists of sheet metal, saidtubular section having an axial cross-section which is longer in anaxial dimension than in a radial dimension and has an axial end surface,said axial end surface being provided with a plurality of tappedrecesses spaced apart from each other circumferentially of said tubularcomponent for connecting a housing to said friction clutch, saidplurality of tapped recesses extending in said sheet metal in an axialdirection of said tubular section.
 15. A torque transmitting apparatus,comprising a composite housing rotatable about a predetermined axis,said housing including a component having an axially extending tubularsection which consists of sheet metal and said tubular section having anaxial cross-section which is longer in an axial dimension than in aradial dimension and which has an axial end surface provided with atleast one recess for connecting a cover to said tubular section, said atleast one recess being formed as a result of displacement of said sheetmetal and extending in said sheet metal of said tubular section. 16.Apparatus for compensating for torsional stresses, comprising a firstflywheel connectable with an engine; a second flywheel connectable withan input element of a transmission, said flywheels being rotatablerelative to each other; at least one damper having means for yieldablyopposing rotation of said flywheels relative to each other; at least oneantifriction bearing interposed between said flywheels; a metalliccomponent having an axially extending tubular section which consists ofsheet metal and is affixed to one of said flywheels and extends in thedirection of an axis of rotation of said one flywheel, said tubularsection having an axial cross-section which is longer in an axialdimension than in a radial dimension and said tubular section having anaxial end surface and at least one recess provided in said end surfacefor connecting a housing to said apparatus, said at least one recessbeing provided in said sheet metal of said tubular section.
 17. Ametallic component constituting an element of a friction clutch andhaving a tubular section of sheet metal, said tubular section having anaxial end surface and said end surface being provided with at least onerecess disposed in a tubularly extending portion of said tubular sectionand being formed as a result of displacement of said sheet metal.
 18. Ametallic component constituting an element of a friction clutch andhaving a tubular section of sheet metal, said tubular section having anaxial end surface and at least one blind bore provided in said sheetmetal at said axial end surface as a result of driving into said endsurface a material displacing tool.